CN217421625U

CN217421625U - Mixed flow fan and ducted air conditioner

Info

Publication number: CN217421625U
Application number: CN202221287510.8U
Authority: CN
Inventors: 丁绍军; 池晓龙; 夏凯; 张一帆
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2022-05-27
Filing date: 2022-05-27
Publication date: 2022-09-13
Anticipated expiration: 2032-05-27

Abstract

The utility model provides a mixed flow fan and tuber pipe machine. The mixed flow fan comprises a volute, an impeller, a front guide vane structure and a rear guide vane structure. The utility model provides a mixed flow fan and tuber pipe machine, through the second interval between first interval and back stator structure and the impeller between injecing preceding stator structure and the impeller respectively, the inlet flow field of impeller can be improved to first interval, reduce the air intake resistance of impeller, the pressure head that second interval can the impeller reaches the requirement of predetermineeing, also can carry out effective water conservancy diversion to the business turn over wind of impeller, guarantee that mixed flow fan's spiral case size can satisfy the pivoted requirement inside the tuber pipe machine, preceding stator structure and/or back stator structure agree with as far as with impeller combustion gas flow direction, further guarantee mixed flow fan's working effect, when the business turn over wind direction of tuber pipe machine changes, mixed flow fan can wholly rotate as required and can not produce with the tuber pipe machine and interfere, thereby guarantee tuber pipe machine's air-out effect.

Description

Mixed flow fan and ducted air conditioner

Technical Field

The utility model relates to an air treatment equipment technical field, especially a mixed flow fan and tuber pipe machine.

Background

The air duct machine is one of air conditioners, in order to improve the comfortableness, some air duct machines adopt an upper cold air outlet mode and a lower hot air outlet mode, waterfall type refrigeration and carpet type warm air can be realized, in order to realize the air outlet mode, the air outlet of the air duct machine is required to be reversible, in the existing air outlet reversible air duct machine, a cross-flow fan and a centrifugal fan are generally adopted, but the fan is not reversible due to the problem of the setting mode of fan blades, the air direction after the reversal is not reversible, therefore, at least two fans can be arranged, one fan is responsible for forward air outlet, and the other fan is responsible for reverse air outlet, so that the structure of the air duct machine is larger, and the cost is higher.

In order to reduce the cost, the fan needs to be reduced, the mixed flow fan is a fan between the axial flow fan and the centrifugal fan, an impeller of the mixed flow fan enables air to do centrifugal motion and axial motion, and the air flow motion in the volute mixes two motion modes of axial flow and centrifugal motion, so that the mixed flow fan is called mixed flow. Moreover, the mixed flow fan not only can reduce the volume, but also can ensure the flow direction and the wind pressure of the airflow.

In the mixed-flow fan in the prior art, the distances between the front guide vane structure and the impeller and between the rear guide vane structure and the impeller are unreasonable in design, so that the mixed-flow fan is low in energy efficiency.

SUMMERY OF THE UTILITY MODEL

The embodiment of the utility model provides an in provide a mixed flow fan and tuber pipe machine to solve the problem that mixed flow fan efficiency is low among the prior art.

A mixed flow fan, comprising:

the volute is provided with an air inlet and an air outlet;

an impeller disposed within the volute;

the front guide vane structure is arranged between the impeller and the air inlet, and a first distance is formed between the front guide vane structure and the impeller;

the rear guide vane structure is arranged between the impeller and the air outlet, and a second distance is formed between the rear guide vane structure and the impeller;

the ratio of the height H1 of the first spacing to the height H of the impeller ranges from 0.1 to 0.21;

the ratio of the height H2 of the second spacing to the height H of the impeller is in the range of 0.18 to 0.24.

The height H1 of the first pitch is less than or equal to the height H2 of the second pitch.

The rear guide vane structure comprises a plurality of guide vanes, and all the guide vanes are annularly distributed by taking the axis of the impeller as an axis; and/or the front guide vane structure comprises a plurality of guide vanes, and the guide vanes are annularly distributed by taking the axis of the impeller as an axis.

At least one be provided with the oscillating axle on the stator, the axis of oscillating axle with the axis of impeller has the contained angle, and has the stator of oscillating axle can use the axis of oscillating axle swings as the axis.

The angle of the included angle is 90 degrees.

The range of the swing angle alpha of the guide vane is 0 DEG to 10 deg.

The front guide vane structure is provided with silencing teeth; and/or the rear guide vane structure is provided with silencing teeth.

The front guide vane structure is provided with a bulge and/or a pit; and/or a bulge and/or a pit are/is arranged on the rear guide vane structure.

The mixed flow fan further comprises an inner shell, the inner shell is arranged between the impeller and the air outlet, an annular air duct is formed between the outer surface of the inner shell and the inner surface of the volute, and the rear guide vane structure is arranged in the annular air duct.

The back stator structure includes a plurality of stator, the first border of stator with the external surface fixed setting of inner shell, the second border of stator with the internal surface fixed setting of spiral case.

The divergence angle of the rear guide vane structure ranges from 10 ° to 40 °.

The outer surface of the volute is a curved surface.

The volute is of a ball table structure, and the maximum diameter of the volute is equal to the diameter of the ball table structure.

The volute is positioned on two end faces of the table structure and is respectively provided with the air inlet and the air outlet.

A tuber pipe machine, includes above-mentioned mixed flow fan.

The utility model provides a mixed flow fan and tuber pipe machine, through the first interval between the preceding stator structure of injecing respectively and the impeller and the second interval between back stator structure and the impeller, the first interval can improve the air inlet flow field of impeller, reduces the air intake resistance of impeller, the second interval can reach the preset requirement by the pressure head of impeller, also can carry out effective water conservancy diversion to the business turn over wind of impeller, guarantee that mixed flow fan's spiral case size can satisfy the requirement of the rotation in tuber pipe machine, the oscillating axle can make the stator of back stator structure swing, make preceding stator structure and/or back stator structure agree with as far as with the impeller exhaust air flow direction, further guarantee mixed flow fan's work effect, when the air inlet and outlet direction of the air duct machine is changed, the mixed flow fan can integrally rotate as required without interference with the air duct machine, so that the air outlet effect of the air duct machine is ensured.

Drawings

Fig. 1 is a schematic structural view of a mixed flow fan according to an embodiment of the present invention;

fig. 2 is a schematic structural diagram of a leading vane structure according to an embodiment of the present invention;

fig. 3 is a schematic structural diagram of a rear guide vane structure provided in an embodiment of the present invention;

fig. 4 is a schematic structural diagram of an impeller provided in an embodiment of the present invention;

fig. 5 is a schematic structural diagram of a guide vane and a swing shaft of a rear guide vane structure according to an embodiment of the present invention;

fig. 6 is a schematic view of a rear guide vane structure and a swing angle of a guide vane according to an embodiment of the present invention;

fig. 7 is a schematic view of a front guide vane structure and a swing angle of a guide vane according to an embodiment of the present invention;

in the figure:

1. a volute; 11. an air inlet; 12. an air outlet; 2. an impeller; 5. a leading lobe structure; 6. a rear guide vane structure; 13. a first pitch; 14. a second pitch; 33. a guide vane; 34. a swing shaft; 4. an inner shell.

Detailed Description

In order to make the objects, technical solutions and advantages of the present invention more clearly understood, the present invention will be further described in detail with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the invention.

In the mixed flow fan in the prior art, when the impeller 2 rotates at a high speed, a negative pressure area is formed at the inlet of the impeller to generate suction, so that gas enters from the current collector through the front guide vane structure. In complex housing environments, adverse air intake conditions tend to develop, and leading vane structures can alleviate such problems. The slender front guide vane forms a narrow air flow channel in the front part of the impeller, and even if a complex flow field exists at the inlet of the current collector, the air flow is rectified into a smoother air flow after passing through the front guide vane structure and then enters the impeller to do work. Because the front guide vane structure does not rotate, a moving and static gap can be formed between the front guide vane structure and the impeller, and meanwhile, in order to reduce the channel resistance, a certain rectifying section (a first interval 13) needs to be reserved to allow gas to freely enter the impeller to do work. The existence of this rectification section is closely relevant with the impeller structure, and the space structure of fan can be wasted to the rectification section overlength, and the rectification section is too short, is difficult to form effectual rectification, can increase the flow resistance of fan on the contrary. Similarly, when the impeller 2 rotates at a high speed, the air flow is driven to flow out of the impeller 2 at a high dynamic pressure and enter a despinning section (the second interval 14) between the impeller 2 and the rear guide vane structure. The rotation-eliminating section can lead the airflow rotating at high speed to be in a horizontal direction from a radial direction, and the sudden pressure relief can convert part of dynamic pressure of the airflow into static pressure for supporting the subsequent flow of the fan. The racemic section, while capable of directing the rotating gas stream horizontally, still carries significant tangential velocities, both of which are detrimental to subsequent flow. The rear guide vane structure has the function of converting more tangential speed of airflow into horizontal speed and converting huge dynamic pressure into static pressure again so as to improve the pressure capacity of the fan. In the prior art, when the energy efficiency of the fan is improved, the structure of the impeller, the structure of the front guide vane or the structure of the rear guide vane are adjusted, however, through the research of the applicant on the airflow flowing principle and the analysis of simulation experiment data, the length of the rectifying section and the length of the despinning section are very important, and the adjustment of the air inlet resistance and the air outlet pressure loss of the impeller is effectively improved, so that the length of the proper rectifying section and the length of the despinning section are very important for improving the system performance of the mixed-flow fan on the whole structure of the mixed-flow fan.

For the above reasons, as shown in fig. 1 to 7, the present application discloses a mixed flow fan, including: the air conditioner comprises a volute 1, wherein an air inlet 11 and an air outlet 12 are formed in the volute 1; an impeller 2, the impeller 2 being disposed within the volute 1; the front guide vane structure 5 is arranged between the impeller 2 and the air inlet 11, and a first distance 13 is formed between the front guide vane structure 5 and the impeller 2; the rear guide vane structure 6 is arranged between the impeller 2 and the air outlet 12, and a second interval 14 is formed between the rear guide vane structure 6 and the impeller 2; the ratio of the height H1 of the first distance 13 to the height H of the impeller 2 ranges from 0.1 to 0.21; the ratio of the height H2 of the second distance 14 to the height H of the impeller 2 ranges from 0.18 to 0.24.

Wherein the portion of the volute 1 corresponding to the first spacing 13 forms the aforementioned rectifying section, and the portion of the volute 1 corresponding to the second spacing 14 forms the aforementioned despinning section. The height H1 of the first distance 13, the height H2 of the second distance 14 and the height H of the impeller 2 are all dimensions in the direction of the axis of the impeller 2, which is the axis of rotation of the impeller 2 during operation.

The simulation test is carried out on the mixed flow fan of the embodiment, the numerical values of the mixed flow fan H1/H and H2/H are changed, and the simulation result is as follows:

according to the simulation data, when the value of H1/H is unchanged and the value of H2/H is smaller, the length of the despinning section is difficult to provide enough pressure release space for the conversion of dynamic pressure and static pressure, so that the pressure head of the impeller 2 is reduced, and the air flow with high-speed rotation speed component increases the diffusion loss of the fan due to the fact that the impeller 2 is too close to the rear guide vane structure 6, and further the whole air volume of the fan is reduced. From the data, it is understood that when H1/H is 0.15, the air volume and the pressure head are relatively small and the diffusion loss is relatively increased when H2/H is 0.17 compared with H2/H is 0.22, which proves that it is difficult to provide sufficient pressure release space for the conversion of the dynamic pressure and the static pressure when the length of the racemic section (second interval 14) is small; when the value of H2/H is unchanged and the value of H1/H is smaller, the front guide vane structure 5 is closer to the impeller 2, airflow cannot be fully rectified, air inlet resistance is increased, the work-applying capacity of the impeller 2 is reduced, and the air volume of the fan is reduced. From the data, it is understood that when H2/H is 0.22, the air volume and the head pressure are relatively small and the diffusion loss is relatively large in the case of H1/H of 0.1 as compared with the case of H1/H of 0.15, and it is proved that it is difficult to provide a sufficient rectifying space for rectifying the air flow when the length of the rectifying section (first gap 13) is small. The influence trend of the appropriate H1/H value and H2/H value on the overall performance of the fan can be fully shown. When the lengths of the H1 and the H2 are both increased, the performance of the fan is also not favorable, because the lengths of the H1 and the H2 are increased while the length of the impeller 2 is reduced under the condition that the size of the mixed-flow fan is fixed, which greatly affects the working area of the fan, so that the performance of the fan is reduced.

The height H1 of the first pitch 13 is less than or equal to the height H2 of the second pitch 14. When H1 is greater than H2, the distance between the front guide vane and the impeller is larger, the gap between the rear guide vane and the impeller is smaller, racemization diffusion cannot be performed sufficiently, and the performance of the fan is reduced. And when H1 is not more than H2, the rear guide vane can obtain sufficient despinning space to carry out pressure boosting on the air flow, and the improvement of the performance of the fan is facilitated.

The front guide vane structure 5 comprises a plurality of guide vanes 33, and all the guide vanes 33 are annularly distributed by taking the axis of the impeller 2 as an axis.

The rear guide vane structure 6 comprises a plurality of guide vanes 33, and all the guide vanes 33 are annularly distributed by taking the axis of the impeller 2 as an axis.

At least one guide vane 33 is provided with a swinging shaft 34, the axis of the swinging shaft 34 and the axis of the impeller 2 form an included angle, and the guide vane 33 with the swinging shaft 34 can swing by taking the axis of the swinging shaft 34 as the axis.

When the front guide vane structure 5 comprises the guide vane 33 and the swing shaft 34, the front guide vane structure 5 is used for making the airflow generate pre-rotation to make the airflow have a certain flow angle, so as to reduce the angle value between the direction of the airflow and the direction when the airflow enters the impeller 2, and finally achieve the purpose of reducing the resistance when the airflow enters the impeller 2, when the impeller 2 works at different rotating speeds, the angle of the airflow entering the impeller 2 is different, when the rotating speed is changed, the angle of the airflow entering the impeller 2 is changed, in order to make the flow angle of the airflow as the same as the angle of the airflow entering the impeller 2 as possible, the flow angle of the airflow in the front guide vane structure 5 is changed accordingly through the swing of the guide vane 33, further increasing the fit degree of the direction of the airflow flowing out from the front guide vane structure 5, thereby being beneficial to the increase of the air intake uniformity of the impeller 2, and ensuring that the impeller 2 can achieve the optimal air volume value at a plurality of working rotating speeds, the mixed flow fan can obtain the optimal air flow driving performance. Preferably, the larger the rotation speed of the impeller 2, the larger the angle at which the air flow enters the impeller 2, and therefore the larger the angle of inclination α of the guide vane 33 is required, whereas the smaller the rotation speed of the impeller 2, the smaller the inclination α of the guide vane 33 is.

The angle range of the pivot angle α of the guide vane 33 is 0 ° to 10 °. Preferably 0 ° to 5 °.

When the rear guide vane structure 6 comprises the guide vane 33 and the swing shaft 34, the rear guide vane structure 6 is used for further guiding the outlet air of the impeller, when the impeller 2 works at different rotating speeds, the angles of the air flowing out of the impeller are different, namely the angles of the air flows entering the second spacing 14 are different, the size of the second spacing 14 is fixed, the despinning capacity is fixed, namely the capacity of changing the air angle is fixed, when the angles of the air entering the second spacing 14 are different, the angles of the air entering the rear guide vane structure 6 are also different, in order to enable the flow angle of the air flows to be the same as the angle of the air flows discharging the second spacing 14 as much as possible, the flow angle of the air flows in the rear guide vane structure 6 is changed along with the swing of the guide vane 33, and the matching degree of the direction of the outlet air flows of the rear guide vane structure 6 is further increased, therefore, the increase of the exhaust uniformity of the mixed flow fan is facilitated, and the mixed flow fan can achieve the optimal air volume value and the optimal airflow driving performance under multiple working rotating speeds. Preferably, the larger the rotation speed of the impeller 2, the larger the angle of the air flow leaving the impeller 2, so the larger the angle of the inclination angle of the guide vane 33 is required, whereas the smaller the rotation speed of the impeller 2, the smaller the inclination angle of the guide vane 33 is. The angle range of the pivot angle α of the guide vane 33 is 0 ° to 10 °. Preferably 0 ° to 5 °.

Wherein the oscillating shaft 34 is angled in the range of 90 deg. to the axis of the impeller 2. So that structural interference with the volute 1 cannot be generated in the swinging process of the guide vane 33, and the structure reliability of the guide vane 33 and the volute 1 is ensured.

The leading blade structure 5 is provided with silencing teeth or bulges and/or pits.

And the rear guide vane structure 6 is provided with silencing teeth or bulges and/or pits.

The noise reduction effect is achieved by utilizing the silencing teeth, the bulges or the pits to carry out silencing.

The mixed flow fan further comprises an inner shell 4, the inner shell 4 is arranged between the impeller 2 and the air outlet 12, an annular air duct is formed between the outer surface of the inner shell 4 and the inner surface of the volute 1, and the rear guide vane structure 6 is arranged in the annular air duct. The inner shell 4 is used for further limiting the air duct in the volute 1, so that the air flow can be better guided by the guide vane 33 when passing through the rear guide vane structure 6.

As another embodiment, the rear guide vane structure 6 includes a plurality of guide vanes 33, a first edge of each guide vane 33 is fixedly disposed with the outer surface of the inner casing 4, and a second edge of each guide vane 33 is fixedly disposed with the inner surface of the volute casing 1. At this time, the guide vane 33 is fixedly arranged between the volute 1 and the inner shell 4, and the fixing strength between the volute 1 and the inner shell 4 is increased by utilizing the rear guide vane structure 6, so that the effect of reinforcing ribs is realized.

The divergence angle of the rear guide vane structure 6 ranges from 10 ° to 40 °. The divergence angle is an included angle formed between a connecting line of a front edge and a tail edge of the rear guide vane structure 6 and a central line of the rear guide vane structure 6 along the flowing direction of gas, wherein the front edge is an air inlet end of the rear guide vane structure 6, and the tail edge is an air outlet end of the rear guide vane structure 6. That is, along the flowing direction of the gas, the size of the cross section of the rear guide vane structure 6 is gradually increased, and when the mixed flow fan is applied, the flow cross section of the airflow entering the rear guide vane structure 6 is smaller than that of the airflow flowing out of the rear guide vane structure 6.

The outer surface of the volute 1 is a curved surface. I.e. the cross-section of the outer surface of the volute is a curved section.

The volute 1 is of a ball table structure, and the maximum diameter of the volute 1 is equal to the diameter of the ball table structure. That is, spiral case 1 can carry out the free rotation in the fixed spherical space of diameter with the centre of sphere of table as the center, when being applied to tuber pipe machine and tuber pipe machine demand when going out wind from top to bottom, can provide the fixed spherical space of diameter for the mixed flow fan that this application provided in the tuber pipe machine, realizes the switching of tuber pipe machine business turn over wind direction through the rotation of mixed flow fan.

The volute 1 is provided with an air inlet 11 and an air outlet 12 at two end surfaces of the table structure.

A tuber pipe machine, includes above-mentioned mixed flow fan.

The above-mentioned embodiments only represent some embodiments of the present invention, and the description thereof is specific and detailed, but not to be construed as limiting the scope of the present invention. It should be noted that, for those skilled in the art, without departing from the spirit of the present invention, several variations and modifications can be made, which are within the scope of the present invention. Therefore, the protection scope of the present invention should be subject to the appended claims.

Claims

1. The utility model provides a mixed flow fan which characterized in that: the method comprises the following steps:

the volute comprises a volute (1), wherein an air inlet (11) and an air outlet (12) are formed in the volute (1);

an impeller (2), the impeller (2) being disposed within the volute (1);

the front guide vane structure (5) is arranged between the impeller (2) and the air inlet (11), and a first interval (13) is formed between the front guide vane structure (5) and the impeller (2);

a rear guide vane structure (6), wherein the rear guide vane structure (6) is arranged between the impeller (2) and the air outlet (12), and a second interval (14) is formed between the rear guide vane structure (6) and the impeller (2);

the ratio of the height H1 of the first distance (13) to the height H of the impeller (2) ranges from 0.1 to 0.21;

the ratio of the height H2 of the second distance (14) to the height H of the impeller (2) ranges from 0.18 to 0.24.

2. The mixed flow fan of claim 1, wherein: the height H1 of the first pitch (13) is less than or equal to the height H2 of the second pitch (14).

3. The mixed flow fan of claim 1, wherein: the rear guide vane structure (6) comprises a plurality of guide vanes (33), and all the guide vanes (33) are annularly distributed by taking the axis of the impeller (2) as an axis; and/or the front guide vane structure (5) comprises a plurality of guide vanes (33), and all the guide vanes (33) are annularly distributed by taking the axis of the impeller (2) as an axis.

4. The mixed flow fan of claim 3, wherein: at least one guide vane (33) is provided with a swinging shaft (34), the axis of the swinging shaft (34) and the axis of the impeller (2) form an included angle, and the guide vane (33) with the swinging shaft (34) can swing by taking the axis of the swinging shaft (34) as the axis.

5. The mixed flow fan of claim 4, wherein: the angle of the included angle is 90 degrees.

6. The mixed flow fan of claim 4, wherein: the range of the pivot angle alpha of the guide vane (33) is 0 DEG to 10 deg.

7. The mixed flow fan of claim 1, wherein: the front guide vane structure (5) is provided with silencing teeth; and/or the rear guide vane structure (6) is provided with silencing teeth.

8. The mixed flow fan of claim 1, wherein: the front guide vane structure (5) is provided with a bulge and/or a pit; and/or a bulge and/or a pit are/is arranged on the rear guide vane structure (6).

9. The mixed flow fan of claim 1, wherein: the mixed flow fan further comprises an inner shell (4), the inner shell (4) is arranged between the impeller (2) and the air outlet (12), an annular air duct is formed between the outer surface of the inner shell (4) and the inner surface of the volute (1), and the rear guide vane structure (6) is arranged in the annular air duct.

10. The mixed flow fan of claim 9, wherein: the rear guide vane structure (6) comprises a plurality of guide vanes (33), a first edge of each guide vane (33) is fixedly arranged on the outer surface of the inner shell (4), and a second edge of each guide vane (33) is fixedly arranged on the inner surface of the volute (1).

11. The mixed flow fan of claim 1, wherein: the divergence angle of the rear guide vane structure (6) ranges from 10 ° to 40 °.

12. The mixed flow fan of claim 1, wherein: the outer surface of the volute (1) is a curved surface.

13. The mixed flow fan of claim 1, wherein: the volute (1) is of a ball table structure, and the maximum diameter of the volute (1) is equal to the diameter of the ball table structure.

14. The mixed flow fan of claim 13, wherein: the volute (1) is positioned on two end faces of the table structure and is respectively provided with the air inlet (11) and the air outlet (12).

15. A ducted air conditioner characterized in that: comprising the mixed flow fan of any one of claims 1 to 14.